Transmission



March 20, 1951 c, GERS-r 2,546,064

TRANSMISSION Filed Jem` 2, 1948 5 Sheets-Sheet l lum INVENTOR.

CHR/S GRST c. GERST TRASMISSION March 20, 1951 5 Sheets-Sheet 2 Filed Jan. 2, 1948 INVENTOR. CHR/S EERST BY v March 20, 1951 c, GERS-r 2,546,064

TRANSMISSION Filed Jan. 2, 194s 5 sheets-sheet s' C. GERST TRANSMISSION March 20, 1951 5 Sheets-Sheet 4 Filed Jan. 2, 1948 INVNOR.

|OW 5 J Patented Mar. 20, 1.951

UNI'I'ED:l STAT OFFICE Transmission;- it?V Geary' Company, Dearborn, Mich.,` a.,corporation:A of MichiganI Application January 2, 1948g1seriarNm1o5 This .invention rel'ates'invv general1to1reversirvg-V shaftz'and ;a.A second berel;pinion;on;a;powerftakaf@ mechanism in which independently rotatable*A oiflshaft, iniwhich the.beveLpinionorrtheginpntr drivingv andi driven members` are; selectively shaftaeiectsrotationofthebevelgears;ingopffY coupledfwith each othery b'ya'fclutch` device, and; positedirectionsgwith,respect to; eachother; andi; more particularly, tosareversi-blev transmission-2 5f inrWhich Athe duaii.friction-clutchrisgmounted v: in whichv driving and'driverrmembers are-'coupledf` the 'intermediate :shaftgmeans andincludesieolutc with .each otherbya'dual/frictionfclutch offthe memberszcoupled Withz-the beve1 ,'gears.tmeiectzs type disclosed in my;copending;applications:serialik the: desired: rotationl of the.:v intermedia-te; shaft No; 728,842'ffiled `February15,` l`947l`and'seria1 No;- and; theioutputzshaft; by; actuationsgof the-dualil 784,681fledlNovember-i'l, 1947. Thisftype ofiidual l0 friction clutch. frictionalclutch-includes a: pressure -plate'struc Still anotherv object off: the;A imlention-l is;v a ture. with* axially-l spaced pressure plates; and `a 1 reversible transmission of the;- typo;y referred; to; backingplatastructure positionedb'etween the# above; which4 is: provided with, brake ,1 means pressure zplates'fr cooperation of thepressure# adapzedto. stop; rotationzoff. the-.dual friction.:- platestructure=withthebacking plate structure i5 sclntch' andicontrollngymeansforitheizclutchxfand.; in selectively actuatingf clutchY disk assemblies the brake.; meanswith the controlling;I/Ileans, ofthel dual 'frictionfclutchfby'shifting of the Ypresarranged'. to;l stop rotationof the clutch `andrin-` Y sure plate structure-infopposite-.directions termedate'V Shaft-When clutching;Y 30171011: 0fr thef The primary-object of'thepresentinvention dualarfrictionzclutch is stopped byr its-scontrolli-ng` theN provision of a.'Y reversible.- transmission f em- 20 rneanssA bodyingf angularly4v related input and output Y Withfthe' abovepand other incidentalfobjisctszsinf shafts coupled,L With each other bygearing; View, lthe invention hasother marked impr-oyes-A intermed-iateshaft meansv and af dual!v friction ments,-` and; superiorities.. which radically. disclutch',` in Which'- transmissiontheintermediatev tinguishfiti from; presently known structures-.. shafimeans-mountstheduallfriction-clutehancl` 25 These improvements or,superioncharacteristics.

clutch members of'the-'dual'friction clutch'are-in embodyirrgacertainnovel features of construction,-l

selective drivingengagement Withsymmetricallyf are; clearlysetfforth in theaappendedclaims; and.. arranged bevel 'gears1 rotatedfirr oppositefdire afpreferred; embodiment offstheinventionis1here-` tion, with respectfto each other; bysthe input" inaftershown'withsreferenceto theaccompanyr, shaft for"selective'rotationofthe intermediate'n inggVdrawingslforming; part' of:V thelvspecication. shaft meansl and theoutput sliafticoupledfthere- Infthe drawings? with: by*` actuation i of the dual friction clutch; Figi, 1f-isfarlongitudinalsectional:view/through. Another objectof the inVen-tionis-the-provision a .reversible rightangle transmission.:constructedf of af reversible transmission embodying angularlyV inaccordance', with the.v invention, thefr section related input: and output' shafts and; an; inter: 35`fbeing taken on line I-I of Fig. Ziof the, drawings.v mediateshaft arranged parallelto theA output; Fig.; 2 is a; .front vieW- of-,. the -reversing ..trans shaft and cou-pled' therewith, in whichv trans.- mission shown in Fig.;` l., mission the intermediate' shaftv is coupledwith Fig3 isfan endfvewof the vtransmission sh.o ,.WI1-.L the input shaftby axially spaced' lbevel gears iii-Eig. 2,7.,the`view,` beingfgtakenfromi line-n 3er-3:, meshing ay bevel pinion onth'einput shaft and' 40 indficated;in.Fig.,2 of thefdrawings.A

rotated by Ysaid bevel pinion. in opposite., direc- Figglliisa sectional View online li-4of.1ig;gl.z tions; and Ainjwhich dual frictionY clutch, means Fig; 5". is a sectional View through the` dual;V are mounted onl the intermediate shaft andinfrictionlclutehiof the transmission,.thessectiony cludes *clutchY members coup1ed with the bevel .v being taken-on: line 5 5 of. Fig,o 1` gears to4 effect the..desired'rotation .of theinter, 45' lig-` 6 islanother sectionalview; through: the mediate shaft andi outputshaft by; actuation of. dual: friction clutch of. the transmission;4` thee the dualfriction clutch means. sectionlbeingtakenon line;-6;of Fig-:1.

Av further object ofthelinvention.y the. pro Fig; 7:is-.an-en1arged;endzviewvoffthe dual,"- vision of areversible transmission embodying friction clutchv showing; thezcoupledf; operating:L angularly related input andoutput shaftscoupled; 50i-meansy for :the clutch andwbrake,l and;

with each other by:V gearing, intermediatefshaft: Fga is asectionalsview, paltlysnlelevatn 011 means and a dual friction clutch, in which trans.- line 8-8= 0f Figs 7. mission the intermediate shaft-:meansfare-ooupled Referringvnowmore1in; detail to thexexempliedf.

with the inputshaftby` axiallnspacedr parallelA formtlofI transmission shownv inc th`e= drawings, bevel gears meshing a bevelpiniononfthefinput 55y1referenceznu-meral,2vdenotesfrightpanglesfreversinga 3 transmission embodying a housing 3, the bell portion 4 of which is adapted to be secured with its flange 5 to the housing of a motor (not shown). Housing 3 rotatably supports at its rear side a short input shaft 6 mounted in a ball bearing 1 and outwardly extended through bell portion 4 for coupling with a motor shaft (not shown) and at its rear end an output shaft 8 mounted in ball bearings 9 and i8 and outwardly extended for coupling with a mixing drum (not shown). The thus journaled input and output shafts 6 and 8 are angularly related to each other and coupled with each other for selective rotation in opposite directions by mechanism hereinafter to be described.

Input shaft 6 is provided at its inner end with a bevel pinion I I extended between and meshing two axially aligned, spaced bevel gears I2 and I4, the axes of which are rectangularly related to the axis of input shaft 6. Bevel gears I2 and I4 are rotated in opposite directions by input shaft 6 and secured to concentrically arranged tubular shafts I5 and I6 of a dual friction clutch structure l1 axially aligned with an intermediate shaft I8 `and mounted on the splined end portion I9 thereof. Shaft I8 is journaled in housing 3 and coupled with output shaft 8 by gearing 26 consisting of a pinion 2l on intermediate shaft I8 and a gear 22 on output shaft 8 meshing pinion 2 I.

The dual friction clutch structure I1 embodies a pressure plate structure 23 and a backing plate structure 24 slidably and non-rotatably coupled with each other for joint rotation with intermediate shaft I8. Pressure plate and backing plate structures 23 and 24 are non-rotatably and axially shiftably interengaged with each other in such a manner that the backing plate structure extends substantially within the pressure plate structure to permit selective coupling of intermediate shaft I8 with either one of two individual clutch disk assemblies 25 and 26 arranged within the pressure plate structure at opposite sides of the backing plate structure.

The pressure plate structure 23 consists of a cylindrical body 21, the peripheral wall 23 of whichis radially slotted to provide body 21 with a plurality of radial slots 28. This body has its one end partly closed by a ring-shaped plate 30, secured to body 21 by bolts 3I, and its otherV end inwardly flanged to provide the body with a flanged portion 32 opposed to ring-shaped plate 36. In addition body 21 includes ear portions 33 integrally extended from the outside face of flanged portion 32.

The thus constructed pressure plate structure is slidably and non-rotatably engaged with the backing plate structure 24 which includes backing plates 34, 35 positioned between the ringshaped plate 30 and the flanged portion 32 of the pressure plate structure and slidably and nonrotatably engaged with the peripheral wall 28 of the pressure plate structure by radial driving lugs 36 extended through the radial slots 29.

vThe backing plate structure 24 embodies a cup-shaped body 31 which is dimensioned to be sleeved upon the body 21 of pressure plate structure 23 and has extended from its wall 38 an internally splined hub member 39 mounting body 31 on the splined portion I9 of intermediate shaft I8. The peripheral wall 46 of body 31 is externally threaded and in addition radially slotted to provide said wall with a plurality of slots 4I sized and arranged to fit and align with the radial slots 29 in the body 21 of the pressure plate struc- 4 ture 23 to permit proper engagement of body 31 with the driving lugs 36 on the backing plates 34, 35. These backing plates extend between the ring-shaped plate 36 and the fianged portion 32 of the pressure plate structure and are held in proper position by adjustment rings 42 threadedly engaged With the peripheral wall of body 31 and held in adjusted position by spring-pressed plunger 43 extended into circumferentially arranged bores 44 in the side walls of adjusting rings 42. Such mounting of backing plates 34 and 35 permits adjustment of the relative clamping position between the pressure plates and the backing plates, and such adjustment is effected by shifting the backing plates to the desired position by rotation of adjustment rings 42 threadedly engaged with the body 31 of the backing' plate structure.

Shifting of the pressure plates in opposite directions to actuate either one of the two clutch disk assemblies 25 and 26, later to be described, is effected by dual clutch levers 45 pivotally mounted on pins 46 which are supported in pairs of parallel ribs extended in symmetrical arrangement from the rear wall 38 of body 31. These dual clutch levers include third lever arms 41 linking the dual clutch levers to the ear portions 33 of the body 21 of pressure plate structure 23 by means of links 48 which are extended through openings 4S in the rear wall 38. The dual clutch levers 45 eachembody a pair of rollers 49 and 55 rotatably mounted between oppositely arranged plates 5I and are actuated by a shifting member 52 which is coupled by a ball bearing 53 with a throw-out collar 54 actuated by a fork 55 on a lever 56 mounted on a shaft 51. lThe shifting member 52 is slidably keyed to the reduced end portion 58 of the intermediate shaft I8 and, when shifted toward the two-way clutch structure engages with its inclined surface 59 the rollers 50 of the dual clutch levers and tilts these levers so as to effect shifting of the pressure plate structure toward the left until the clutch disk assembly 25 is tightly gripped between ring-shaped plate 36 and Vbacking plate 34. When shifting member 52 is shifted in the opposite direction, away from the two-way clutch structure, rollers 56 engage the oppositely inclined surface 6I of the shifting member and tilts the dual clutch levers so as to effect shifting of the pressure plate structure toward the right until the clutch disk assembly 26 is tightly gripped between flanged portion 32 and backing plate 35. Coupling of the two-way clutch structure with the input shaft 6 is effected by the clutch disk assemblies 25 and 26. Thus, clutch disk assembly 25 includes friction driving disks 62, nonrotatably and axially shiftably engaged with the enlarged splined end portion 66 of tubular shaft I6, which is coupled with bevel gear I4 and concentrically encircles the tubular shaft I5 and intermediate shaft I8, and a friction driven disk 64, non-rotatably and axially shiftably engaged with the internally toothed peripheral wall 23 of body 21; and the clutch disk assembly 26 includes friction driving disks 65, non-rotatably and axially shiftably engaged with the enlarged splined end portion 63 of tubular shaft I 5, which is coupled with bevel gear I2 and concentrically encircles the intermediate shaft I8, and a friction driven disk 61 non-rotatably and axially shiftably engaged with the internally toothed peripheral wall 28 of body 21.

The tubular shaft I5, which is the forward drive shaft, is keyed to bevel gear I 2 and ac' tuates the intermediate shaft I8 when the clutch disk assembly 26 is actuatedfbyvmoving the-shift.- ing.:y coneA or. member. 52., awayf from theclutch structuretostightly grip this.. .clutch diskassembly;between:- t-hellanged portionqaz and. backing plate 35.- In thiscaserotatiom ofinputrshaftt is-transferrediover. bevel gearsI'Z; tubular; shaft I; clutchrdisk assembly.26 .body.3 1 andrits; hub member 39 tothe intermediate.. shaft I8 and hence through gearing 20'to the output shaft 8.

Thetubular shaft I6, whichis the reverse drive shaft is :keyed .tobevel-i'gear: Ixifiiand actuates. the intermediate' shaft.. liwherr the-".clutchzdisk'xassembly 25 is actuated by moving shifting cone or member 52 toward the clutch structure to tightly grip this clutch disk assembly between the ringshaped plate 30 and backing plate 34. In this case rotation of input shaft e is transferred over bevel gear I4, tubular shaft I6, clutch disk assembly 25, body 31 and its hub member 39 to the intermediate shaft I8 and hence through gearing 2U to the output shaft 8.

In the described two-way clutch structure the clutch disk assemblies cannot be actuated upon simultaneously and, therefore, a change of rotation of output shaft 8 can be effected without damage to the rotary parts. To more effectively stop rotation of the clutch structure during quick shifting operations, there is provided a brake mechanism 68, the brake band 89 of which embraces cup-shaped body 31, see Figs. 'l and 8.

Brake band 69 has its one end l@ connected to housing 3 by an attachment member 1I which is secured by bolt 12 to a stud 13 on said housing and is coupled with the end 1I) of the brake band by a pin 14. The other end 15 of brake band S9 is coupled with one arm 16 of a bell crank 11 pivoted on a bolt 18 secured to another stud 19 on housing 3 to effect tensioning of the brake band when bell crank 11 is pivoted upwardly by engagement of its other arm 8i! with the cam portion 8l of an axially shiftable cam rod 82 slidably mounted in the cylindrical bore 83 of a stud 84 on housing 3. This cam rod is shifted by a fork-shaped lever 85 secured to shaft 5l for simultaneous cooperation with lever 56 actuating dual friction clutch structure I1. The cam porbtion2 8| of cam rod 82 embodies two spaced, cutout portions 86, 88 and a slightly grooved portion 81 arranged between the cutout portions and cooperates with a roller 88 on arm 80 of bell crank 11. Thus, in neutral position of the dual clutch structure I1, roller 88 rests on the grooved portion 81 to effect braking action of brake band 69 and in forward or reverse position of the dual clutch structure I1 roller 88 rests in one or the other of the cutout-portions 86, 86' to fully release any braking action of brake band 69.

The described reversing transmission, which forms a compact and simple unit, is economical in manufacture and service as the two-way clutch structure which is covered by a hoodshaped cover member 95 is freely accessible due to its outside location.

Preferably the described reversing transmission incorporates a power take-off shaft 89 for driving a pump or any other device. This power take-off shaft is rotated with the same speed as the input shaft 8 and for such purpose has its inner end provided with a bevel pinion 90 extended between and meshing the bevel gears I2 and I4. The power take-off shaft is journaled in housing 8 by ball bearings 9|, 92 and freely, rotatably supports a pulley 93 adapted to be selectively coupled with the power take-off shaft by a single disk clutch 94.

Having thus described mysinvention;.whatailiber, dual friction clutch means,- anxintermedate rotary member geared at its `oneend to said driven member and mountingmn its other end said, dual friction clutch means, shifting means to; selectively. actuate the clutch .members of said duat friction` clutch means, and" a power. takeoff"sh`aft`arrangedbetween and directly driven by said bevel gears said dual friction clutch means including driving clutch members secured by tubular members to said oppositely rotating bevel gears and driven clutch members secured to said intermediate rotary member and said dual friction clutch means being adapted to effect rotation of said intermediate rotary member and the driven member geared thereto in the desired direction by selective shifting of the shifting means for said dual friction clutch means.

2. In a reversible transmission a drive shaft, a driven shaft, two axially aligned, spaced rotary members havingA their axes rectangularly related to the axis of said drive shaft and driven thereby in opposite directions, an intermediate shaft geared with its one end portion to said driven shaft and axially aligned with said rota-ry members, a dual friction clutch means, including a backing plate structure rigidly mounted on the other end portion of said intermediate shaft in laterally offset relation to said rotary members, brake means encircling said backing plate structure, actuating means for said dual clutch mechanism shiftable in opposite directions, axially aligned tubular members keyed to said rotary members and slidably and non-rotatably supporting at their free ends driving clutch members and driven clutch members slidably and non-rotatably supported by said backing plate structure and adapted to cooperate in clutching operations with said driving clutch members, said actuating means when shifted in opposite directions eifecting selective coupling of said intermediate shaft with either one of said rotary members, and coupling means connecting said brake means with said actuating means for braking action on said backing plate structure when said dual clutching means are in neutral position.

3. In a reversible transmission a housing, a first shaft in said housing extended therefrom through one wall thereof, a second shaft in said housing angularly intersecting the axis of said first shaft and extended from said housing through another wall thereof angularly related to said first wall, two spaced, oppositely arranged bevel gears axially aligned with respect to said rst shaft for rotation in opposite directions, dual friction clutch means mounted on the outwardly extended end portion of said second shaft, said dual friction clutch means including a backing plate structure and driving clutch members coupled with said spaced bevel gears by tubular shafts encircling said second shaft, said' backing plate structure including a cup-shaped housing rigidly mounted on the extended end portion of said second shaft and backing plate means supported by said housing, brake band means encircling the said cup-shaped housing and actuating means for said dual friction clutch means coupled with said brake band means for actua- 7 tion of said brake band r-neans in predetermined Number position of said dual friction clutch means. 1,609,782 CHRIS GERST. 1,788,938 1,887,789 REFERENCES CITED 5 2,323,753 The following references are of record in the 1330295 le of this patent: 2,379,023

UNITED STATES PATENTS Number Name Date 10 Number 687,474 Broberg Nov. 26, 1901 341,177 1,130,134 Baldwin Mar. 2, 1915 473,229 1,136,279 Severy Apr. 20, 1915 Name Date Small Dec. 7, 1926 Zetterlund Jan. 13, 1931 Rush Nov. 15, 1932 Jaeger July 6, 1943 Lundberg Sept. 28, 1943 Miller June 26, 1945 FOREIGN PATENTS Country Date Great Britain Jan. 15, 1931 Great Britain Oct. 8, 1937 

